Spiral vibratory conveyor



March 18, 1958 TAKUzo TsUcHlYA ETAL 2,327,157

SPIRAL VIBRATORY coNvEYoR Filed March 10, 1954 6 Sheets-Sheet 1 2 a/\ f 37 /o t a u l INVENToR.

March 18, 1958 m-Kuzo TsUcHxYA ETAL v 2,827,157

SPIRAI.. VIBRATORY CONVEYOR Filed March l0, 1954 6 Sheets-Sheet 2 'Flg 3 'Ill ; www am fr0/Wvg Y March 18, 1958 TAKUzo TsucHlYA ETAL 2,327,157

SPIRAL VIBRATORY coNvEYoR 'Filed March 1o, 1954 e sheets-sheet s 'IllIt f- 56 43 l--ln-Il, JNVENTOR.

Zafra/Z@ IFM/wwwa @f l @ma March 18, 1958 vTAKUZO TsUcl-HYA ETAL 2,827,157 I SPIRAL VIBRATORY CONVEYOR 6 Sheets-Sheet 4 Filed March 10, 1954 n N M .n A

@gewag lav@ March 18, 1958 TAKUzo TsucHlYA ETAL' 2,827,157

snm. VIBRATORY coNvEYoR Filed March 1o, 1954 .e sheets-sheet 5 IN V EN TOR.

Wilke/2a KSJ/@wm 65mm@ las@ y I f 25'0-k Y ArroPMe-Y March 18, 1958 TAKuzo TsUcHlYA ETAL 2,827,157

SPIRAL VIBRATORY coNvEYoR Filed March 1o, 1954 e sheets-sheet e IN VEN TOR.

fsm/zo knew/A @zz-wmf lla/v6 @y Afro/@wey United States @arent ernaar vraanroav eoravnvon Tanuzo Tsuchiya and George Long, Minneapoiis, Minn., assignors to General Miils, inc., a corporation of iiela= ware Application March lil, i954, Serial No. ill- 24 Claims. (fili. 19d-22%) The present invention relates to improvements in vibratory conveyors and more specifically to an improved system for imparting a vibratory movement to a helical conveyor to carry a solid material along a helical path uually from a lower to a higher elevation.

Conveyors which carry solid material upwardly along a spiral or helical path have been previously known to the conveying art. These conveyors are given a vibration moving the conveyor in a rotary oscillation about the conveyor axis which has a vertical component of movement to cause the material to travel uphill along the spiral path and to be discharged at a higher level. lt will be appreciated that in such a conveyor which is to operate continuously the vibratory force may impart a considerable vibration to the conveyor support and considerable wear to any moving parts. Further, because of the severe vibrations required, the parts normally must be made relatively heavy so that failure of the related structural parts does not occur. This of course increases the bulkiness of the machine and also increases the expense considerably.

Further, because of the vibrations transmitted to the support such as a building floor, it is frequently impractical to use this type of conveyor unless the building and door are extremely rigid and have considerable mass.

in these vibratory conveyors the vibratory force is frequently applied directly to the conveyor with the conveyor being spring mounted to permit it to vibrate. rl`he vibrations are assimilated by springs but equal and opposite reactant forces are transmitted to the supporting base or stand causing a vibration of the base and the floor. In other conveyors the vibratory force is obtained by a direct mechanical connection between a vibrator which is mounted on the base or the iloor and the suspended conveyor. This again creates reactant forces which are transmitted by the vibrator to the base or the floor.

it is accordingly an objective of the invention to provide a spiral vibratory conveyor in which very minimum vibratory forces are transmitted to the support and the forces are assimilated in the mechanism itself without the creation of equal and opposite reactant forces which must be transmitted to the supporting base or tioor.

A further object of the invention is the provision of a spiral vibratory conveyor which is supported by spring beams which are secured to an intermediate base with the intermediate base in turn supported by other spring beams.

Another object of the invention is to provide a spiral vibratory conveyor in which the conveyor is solely supported by spring beams extending at an angle to the helical path of the conveyed material and connected from an intermediate base which carries a cyclical torque applying means to vibrate the conveyor with the intermediate base being supported by other spring beams projecting substantially vertical from either a floor or overhead support.

Another object of the invention is to provide a helical conveyor in which vertical forces are counteracted so 2 that they are not transmitted to the building in which the conveyor is supported.

A still further object of the invention is to provide a spiral vibratory conveyor which is supported by spring beams secured to an intermediate base which carries both an apparatus for creating a cyclical torque about the conveyor axis and au apparatus for creating a vertical cyclical force to counteract and cancel vertical inertia forces of the conveyor.

A further object of the invention is to provide a spiral conveyor system supported on an intermediate base with an improved set of spring beams extending between the intermediate base and the conveyor which will greatly reduce or minimize the effects of twist and will have a longer operating life.

Another object of the invention is to provide a force applying means for the intermediate base supporting the helical conveyor on springs which creates a cyclical torque about the axis of the conveyor and an additional vertical cyclical force to cancel the vertical inertia forces of the conveyor with the ratio between the torque and vertical forces being adjustable.

Other objects and advantages will become apparent in the following specification taken in connection with the appended drawings in which:

Figure l is a perspective view of the spiral conveyor assembly illustrating one embodiment of the invention;

Fig. 2 is a sectional view taken along line 2-2 of Fig. l;

Fig. 3 is an enlarged View of the upper portion of the conveyor of Fig. l;

Fig. 4 is a perspective view illustrating another embodiment of the invention with means provided for annulling the vertical inertia forces of the conveyor;

Fig. 5 is a perspective view of the conveyor of Fig. 4 showing it suspended from a ceiling support;

Fig. 6 is a more detailed view of the upper portion of the conveyor of Fig. 4;

Fig. 7 is an enlarged detail of the mechanism which enables adjusting the angle of the axis of the rotating unbalanced weights to adjust the ratio between the forces creating a torque and a vertical force;

Fig. 8 is an enlarged detailed view of the ends of the improved spring beams;

Fig. 9 is another enlarged detailed view partially in section to illustrate the manner of securing the spring beams to the conveyor or to the intermediate base;

Fig. 10 is a diagrammatic view illustrating the path of movement of the conveyor spring and the inertia forces of the conveyor; and,

Fig. ll is a perspective View of another embodiment of the principles of the spiral conveyor of the present invention.

As illustrated in the drawings, the present invention is designed primarily for use for conveying materials from a lower to a higher level through a spiral or helical path.

One form of the spiral conveyor is shown in Fig. l. The material enters the spiral conveyor at 20 to be conveyed upwardly in a helical path following the arrows 22. When the material has circled upwardly to the top 24 of the conveyor column, it is discharged through the discharge spout 26 into a receiving container 28.

The material is caused to be moved upwardly by the vibrations of the conveyor, shown generally at 30, which take the form of rotational oscillations in which the forward or backward movement of any point on the conveyor moves at an angle steeper than 0 (shown at 64), which is the angle of incline of the helix 32 which forms the floor of the conveyor. This movement causes the material to be thrown upward and forward with each forward movement of the conveyor so that it moves upwardly along the spiral contines of the conveyor. The

' by the angle at which movement Yof the conveyor is illustrated by the arrows 66 shown in Fig. l. It will be seen'that this path of movement is at right angles to the tops of the springs 5,2, 54 and V576, which 4remain substantially stationarytat their lower ends. Y Y i Although the conveyor Yis designed primarily for conveying materials uphill, it maybe putV to other uses following the; principles of the invention. For example, the conveyor may be designed to convey materials downhill Yatfa controlledrate;V 'In that case the 'conveyor willrnove upwardly and backiin Vits rotary oscillating vibrations at an angle less than 0, as shown Aat 64 in the drawings. This angle at which the conveyor vibrates is determined the supporting spring beams 52, 54 and 56 `are connected to the conveyor as will be later explained. Y

The bonveyor tube for carrying', the material may be described in Fig. l as comprising a'cylindrical tube 3i which may be formed of sheet metal or'similar suitable material. The tube surrounds a Vsheet'metal door 32 which -isA cut in a--helix to denne ak spiral path winding upl V-wardly around a central ycolumn 34 which extends the full height of the conveyor tuberand is located concen- Ytrically withiny the outer shell 31. The top and bottom ends of the outer shell are closed by circular discs 36 Iand 37 of material with the central column 34 being attached at the center of the discs.l

In Fig. 4 lan alternate form Yof helical conveyor tube is Y shown.. The conveyor tubes or elevators illustrated are shown for purposes off example only audit will be apparent later inthe specification that the invention is not limited to any particular type of spiral conveyor but may be used with various forms.

The conveyor of Fig. 4, Vagain shown generally at the numeral 130, has-a central cylindrical` column 36 about which a conveying channel38 ishelically wrapped. The

channelsis comprised of a Ifloor 40 slanting helically up ward and lan outerverticalconning wall 42 secured at the outer edge-of the helical floor.

wall being the center column 36. A feeder pan 43 is located at the bottom ofthefconveyor to receive material from a supply yspout '44. VAv delivery spout 46 is attachedfat the top of the conveyor 30 to deliver the material to bin 28. e 'Y Next willbe described-the structure which supports the conveyor land the devices which give'theconveyor its vibratory motion and which function to balance out the vibrations and acceleration forces sothey are not transmitted to the building in which the conveyor is housed. These supporting,0perating, and vibration reducing elebrate for conveying; an intermediate base which carries Vthe spring beams and (which also Ycarries a cyclical torque applying means to give vibratory movement to the conveyoralndla'force applying means to cancel the reactance `forcescrandja second set of spring beams to support the intermediate base from the oor or ceiling of the building. From ltheabove structure the system may be gen- Verallytermeda two-mass,two spring helical conveyor. Th'econveyor and intermediate base comprisethe two masses andthe first spring beams supporting the'conveyor 'from' the intermediate base, and the second spring beams Y The vertical wall 42 comprises'the Aouter wallet the channel with the inner i basek member is indicated generally V-ments of the conveyorY are the nrst rset of inclined spring beams'wh1ch support the conveyor and permit it to vibodiment the supporting and operating mechanism is arranged around the spiral conveyor tube and the conveyor therefore can extend for some distance past `the operating mechanism. This is advantageous in instances where head room is at a premium such as where the conveyor discharge must be near the ceiling. In this arrangement the mechanism can be neatly arranged around the conveyor tube and can be located in a remarkably small space. u

To support the conveyor from the intermediate base 4S a first set of spring beams is provided. In the simplilied construction the set of beams includes three flattened springs 52, 54and S6 which are rigidly clamped at their bottom ends to the annular ring 50 and at their upper ends to a circular flange 58 which is secured to the conveyor tube for Supporting it. Each end of each of the spring beams is clamped to the ange 58 and also to the intermediate base 48 by a casting assembly rand only one need be described. The-casting assemblies such as that shown at 60 in Fig. 3 have a bracket`59 which is rigidly secured to thellange S8 such asv by bolts 61 and has the spring beams secured to it by bolts 63, the bolts also extending through the angle block 64. YThe angle of the bracket 59 and shape'of block `64 determine the angle atwhich the springs are .connected to the conveyor and of the conveyor. YA similar for each end of the spring hence the angle of vibration casting assembly is provided beams 52., 54V and 56.

While both Vends of the spring beams are shown rigidly connected, it is'only necessary that kone end of each spring be secured and pivotal connectionsycould be used at the other ends. In such a case, however, four times the number. of spring Vbeams would be needed for the same resilience.

Thus, the first set of spring beams provides the sole supporting or weight bearing connection between the conveying member andV intermediate base. It will be noted that the spring beams are inclined. The angleof beams is such-that the beams are inclined with respect to the path of feed ofrnaterial. To put it another Way, the angle of the beam 52 Vin Fig.Y l 'issuch that the path of movement of the conveyor floor, as indicated by the arrows 66, willbe at-a greater anglethan the angle of incline 0 of the lconveyor oor. Thus the angleof the beams with `the vertical is also greater than 'the angle 0. ThisV causes the materialV to be thrown upward and tor- .ward when the conveyor .vibrates Thus the -path of vibratory movement of the conveyor isV dictatedrby Vthefpathof movement ofithe upper ends of the vspring beams 52, the intermediate base 4S remaining relatively stationary during the conveying operation. The'vibratoryrnovernent of thel conveyor tube is 'in the form of Van Vupward and -forward and downward Vand backward rotary oscillationgabout Vthe central axis offthe helix.

The actual'path of -rel'ative movement is Ymore in the nature of an arc, but-tor'srnalldisplacements ofvibration ness increases their ystrength so that they will not buckle with theweight of theyconveyor. These rods `or second set of spring beamsa, 76 and y72 are secured to the intermediate base by rigid 'clamps 76, 78 and r8i), respectively. The k factor of `the `beams or stillness factor considering'thern as springs, is important land will be Vdiscussed later. The beams -eXtend vertically fromV the intermediate base to a suitable support baseill which rests lon the lloorZ Yof ythe lbuilding. Y Thejbeams'or rods of .course lmay Abe'anchore dtlire'c'tly to tlietloor but asshowm the conveyor may be transported from place to place to comprise a self contained unit.

Although the second spring beams are vertical, in some cases other supports for the intermediate base would be acceptable. Supports which carry the intermediate base and which are resilient to torsional forces on the intermediate base are operable where no forces are present which would tend to cause a tipping of the conveyor about a horizontal axis.

According to the preferred form of the present invention, the Vertical rods or second set of spring beams are non-extensible and non-compressible in a vertical direction thus preventing any rocking of the operating mechanism and conveyor to result in unstable operation which might possibly tip over the entire conveyor. With respect to this point, it may be said that the spacing of the lower vertical beams or rods from the conveyor axis and size of the annular ring forming the intermediate base is a matter of design out it should be such that the conveyor will not accidentally be tipped. This is of course dependent upon the height of the conveyor, the position of the center of gravity, etc. Further, the overall k, which is the torsional k, of both the upper rst set of spring beams and the lower second set is dependent on their distance from the axial center of the conveyor.

in general the spring constant k2 for the lower springs should be small to reduce the horizontal forces and to displace the first critical frequency of the system toward the lower end of the frequency range. This reduces the chances of undesired vibration as the machine is shut down and the frequency decreases. ln case of large product damping or other damping, a smaller resilience k2 will reduce the force transmission to the foundation. At the same time, however, this resilience k2 of the lower springs must be great enough to support the system as a whole. Within these general principles, the spring constant k2 should be less than the spring constant k1 for the first set of springs, and preferably less than one-fourth of the spring constant k1, while in general, the masses mi and m2 of the conveyor and intermediate base are of the same order of magnitude.

To obtain the desired vibration of the conveyor, which as before stated is in the form of a rotational oscillation with the movement of the conveyor being perpendicular to the angle of the first set of spring beams, suitable force impulses are applied solely to the intermediate base member. This force is obtained by a self contained device capable of applying a cyclical torque obtained from cyclical forces tangential to the path of feed of the conveyor tube.

An illustration of an apparatus for applying such a torque includes a pair of rotating unbalanced Weights S4 and 35, Figs. l, 2 and 3, which rotate on vertical shafts 2 9i?. Slots 92 and Se are cut in the annular ring 5b so that the weights will have freedom of rotation. A pair of guards 96 and 9S may be secured to the annular ring to extend around the Weights to protect personnel.

For driving the weights the lower ends of the shafts 53 and 9G are provided with pulleys 10i) and 110 which are driven by belts liz and 114 respectively. These belts are of the type known to the art as timing belts in which the pulley will be positively driven so that the two weights S and S6 will be kept in the proper phase relationship. The belts are driven from pulleys 116 and 118 mounted on a common shaft lZ. All the shafts are suitably supported on bearings on the ring 50 of the intermediate base. The shaft is driven by V-pulley 119 driven by V-belt 122, which in turn is driven by V-pulley 24 carried on the shaft of motor Z. The motor is supplied with electricity by a suitable cord, not shown. For adjusting the speed at which the weights rotate and apply the torque to the intermediate base the speed of the motor 126 is controlled or the speed of the weights is properly adjusted by previous choice of sizes of driving pulleys.

The weights 84 and 86 rotate in the same direction 180 out of phase. As may be seen by studying Fig. 2, the forces of the weights cancel out in a radial direction but augment each other tangential to the conveyor axis, thus applying a reversing torque about the central axis for each revolution of the weights.

According to the invention the frequency of torque irnpulses applied to the intermediate base 48 is adjusted approximately in the range of the natural frequency of the system. The system includes the conveying member Si) and the first set of supporting spring beams 52, 54 and 56.

The natural frequency of the system is dened by the formula where k1 is the torsional spring constant of the upper spring beams and l1 is the moment of inertia of the effective mass of the conveying member and the first spring beams about the vertical axis through the center of gravity of the conveyor.

By operation at exactly this frequency it is theoretically possible (by ignoring frictional or product damping and other factors) to reduce the oscillating movement or horizontai movement of the intermediate base 43 to zero. ln other words, the horizontal or torque applying components of force applied by the eccentric Weights S4 and 86 will be balanced or neutralized at any given instant by equal and opposite forces resulting from the relative deflection of the rst set of spring beams along said inclined rotational path 66 and the conveying member 3d. In this way forces applied to the intermediate base member 48 result in the desired conveying vibrations of the conveying member 39 without substantially horizontal rotation or movement of the intermediate base 4S.

To the extent that this intermediate base 48 remains stationary no torque or other horizontal force impulses will be transmitted to the foundation 82 by the second set of supporting spring beams 63, 7i) and 72 since such springs will remain undeected.

In actual use a system of the type shown in the drawings which show examples embodying the present invention involves not only pure primary forces such as those applied by the unbalanced rotating weights 84 and 86 and the motion of the conveyor, but involves secondary forces due primarily to the material carried on the conveyor and which may be considered as frictional or damping in nature. These additional effects may result in some vibration or rotational oscillation of the intermediate base 48 and may require operation of the rotating unbalanced weights at a frequency slightly different from the above so-called natural frequency of the system. The direction and extent of this Variation in the force frequency can be readily determined in a given case either by consideration of the theoretical analysis given below or by simple test in actual operation.

We have stated that 'I T1 is the undamped natural frequency of the llkl system. lf there were no damping whatsoever, the amplitude of vibration or oscillation of the intermediate frame would be zero when the forced frequency was made equal to this undamped natural frequency.

In practice, such an ideal situation is never quite met, since damping will always be present to a greater or lesser extent. Because of this damping, which may be due to product load, air resistance or other factors, the vibration of the intermediate frame canot be reduced to zero in all cases.

Yet if the damping is relatively small compared to asentar damping constant C is not greater than 0.25Cc, where C`- critica l damping=2\'/k111, and depending to some extent on Vthe actual ratios of I1 to I2 and k1 to k2), there will generally be a particular value or range of values of the forced frequency, in the `immediate vicinity Vof the undamped natural frequency, at which the vibrations of the intermediate base will have a denite minimum. We

havegobserved that thisparticular value of the forced frequency is generaly different from, and in fact some- Vwhat less than the undamped natural frequency.

On the other hand, if the damping is relatively great compared tothe critical damping, the situation may be 'quite different and there lmay be no such Well defined minimum. It may even be dicultV in such a case to achieve good conveying faction of the Working member. The damping we speak Vof vhere is the total damping in the system. This may be considered to include all types yof damping as well as Ythe mass 4eiect of the product being conveyed.

`Thus if large values of'damping are anticipated, much cany be done to improve vthe operation and minimize the vibrations of the intermediate base, 'the horizontal forces transmitted to the foundation, and thewear and tear on the forceapplying mechanism, by a careful selection of design parameters. In other words, the'adverse effect of damping can be reduced by making the product of k times lI as large as possible, consistent with other design conditions, and thus Vkeeping the critical damping high as comparedto actual damping.

VIn'operatiomthe vibratory Vconveyor is first set to operate'without load, at the undamped natural frequency.

The'forced frequency Yis then'adjnsted in the neighbor Y hood of this natural frequency with Vthe conveyor under norrnal'load.V Y The iinal working frequency is then chosen fon the basis of the minimum motion of the intermediate base which is consistent with good conveying action of the Working member.

It is desirable in any case that the lower spring beams 68, 70 and 72 have a sufficient vertical or longitudinal VVrigidity so that theyv prevent tilting or Vleaning of the conveyor. Vlt will be apparent from the path of'movement of the conveyor 36, as indicated by the arrows 66,

that Vthe conveyor moves'. up and down in its vibrations.

The veltical acceleration ofthe Vconveyor exerts force due to the inertia of the mass which is not compensated for. In this embodiment this vertical acceleration force is transmitted through the lower set of spring beams to the voor 82. In other modifications, as shown in .later drawings, a Vmeans is provided to compensate for this vertical force.V Therefore the stiffness of the lower supporting beams must be adequate' to support the weight of the Vconveyor without buckling and also to withstand these vertical.. inertia forces.

in the embodiments of Figs. 4 and 6 the conveyor 30 is again supported'from'thefloor-by a set of supporting spring 'beams 176,V 178. and 1.8i).Y These beams which will be referredto as the second set of beams to correspond with the disclosure of the rst embodiments, extend from a suitable suport 182 on the iioor 184 and are rigidly secured to the intermediate base 186. The intermediate base in this instance, instead of being in Vfthe form of an annular ring as in the case of Figs. 1 and 3, is in the shape of a drum. A stitfening member 187 may be added to connect the three spring beams 176, l17S and 1S0' to reduce possibility of VVibration during operation. .Y

In Fig. the vibratory conveyor and its associated apparatus is shown suspended from an overhead support such as the ceiling 131). rl'he'second set of beams A132, 134 and 136 are anchored to the ceiling in contrast to Figs. 'l-3or 4 and 6 wherethesecond set of beams supports the conveyor from the floor. fit Ywillbenoted in thisinstancethat'the k'factor of thisfsecond set= of beams to prevent Ythe beams from .bending Vwith the Weight of :the conveyor and load need not be ,considered `Since ,the

weight of the conveyor pulls downwardly on the spring beams 132, 134 and'136, they need only sufficient tensile strength tocarry the weight ofthe conveyor and its op.- erating mechanism Aand to keep away om harmonic frequencies.

At the lower end'of the spring beams 132, 134 and 136 is attached the intermediate base 140., To support the conveyor from the intermediate base 140 a rst set of spring beams v142, 144 and 146 are suitably secured at their upper ends to the lower surface of intermediate base 141) and at .their lower ends to a projection 148 at the top of the conveyor 3i). `With the exception ofthe ceiling support vthe structure of the .conveyor .of Fig..5 is substantially the .same as .that .of Figs. 41and 6. Y

The conveyor'of Figs. v4 and 6 is supported from the To secure the spring beams to the drum, arms 194 in Y Fig. 4 or 195 in Fig. 6, extend outwardly from the intermediate base and the spring beams are attached at the ends of the arms. The arms 194 Vand 195 illustrate dilferent typesof arms for performing the same function of attaching the upper ends of the spring beams to the drum 1%. The arms may be welded to the dmm in any suitablemanner and straight arms as shown in Fig. 4 or fabricated bent arms as shown in Fig. 6 may be used.

Arms 196 extend outwardly from` the conveyor to which theY lower ends of the spring beams'are connected. lt is not critical as to how far the rst spring beams are located from the axial center of the conveyor except that their Ioverall torsional k is dependent on their radialv distance from the center. As the spring beams are brought in closer stiffer springs must be used and if they are positioned further from thev axial center, a spring r`having a lower linear k may be employed. The linear k of individual springs which is chosen in design is de` pendent on their -distance from the conveyor axis since the torsional k isequal to the linear k times therdistance obtaining the desired movement of the conveying member v3i), a set of rotating unbalanced weights are provided.

T he unbalanced Weights consist of discs 193, 20G, 262 and .Ztifwith weights 2.@6 shown mounted on the outer edge of .the discs. The weights2l6 may be carried on either side ofthe discs as may be seen by comparing discs 202 and '21194` of Figs. 4 and 6. One pair of discs 198 and 206 is carriedon a shaft 268 and the other pair 202 and 204 is carried `on a shaft 216. These shafts are driven through bevel ,gears 212 and 214 respectively by a cross shaft 216i carrying'bevelvgears 218 and 221) on its outer ends. vThe casing for the drive Vgears is omitted for clarity in Fig. 4 and is shown in dotted lines in Fig. 6, whereas'Fig. 7 shows this structure in detail.

v'The entire vmechanism for applying the cyclical forces Y to the intermediate base is supported on the base. The shaft26r-is suitably carried for rotation on the intermediate'base -and is given Arotation by means of Va V-belt 'i219 driving a pulley v221 on the shaft 216, the belt being driven bya pulley 222 on the driving motor 224. VAgain as in previous'embodiments,.the speedof the motor may 'be controlled Vor else the drive ratio of the timing belt and pulleys and gears is chosen suchthat the unbalanced weights rotate at the -natural frequency ofthe system.

in certain instances mechanism may be provided to be able to make adjustments to the speed of the motor to arrive at the optimum frequency during operation. The pairs of discs carrying the weights 2% rotate in the same direction but each pair is 180 out of phase with the other. Thus the horizontal forces of unbalance cancel out in a radial direction and augment each other tangential to the conveyor to obtain a cyclical torque.

An important feature of the rotating weights of Figs. 4 and 6 is that their axis of rotation is canted or set at an angle to the vertical axis of the conveyor. Thus, when the unbalanced weights rotate they not only exert a' cyclical horizontal force to produce a torque about the vertical axis of the intermediate base, but they also exert a vertical cyclical force. Since the unbalanced weights rotate at the natural frequency of the system and their force is applied when the conveyor reaches the maximum limits of its travel or oscillation in each direction, these vertical forces are applied when the acceleration forces of the conveyor are maximum, i. e., the forces caused by the reversal in direction of movement of the conveyor as it vibrates.

Fig. l shows the locus of travel 236 of the lower end of the spring beam i3d which is attached to the conveyor. The conveyor at its maximum forward movement reaches the point indicated by the arrow 232. At this point the material on the conveyor has been thrown forward and the conveyor is about to begin to reverse its travel. Also at this point the rotating unbalanced weights ld, 2%, 2%2 and 264 exert the force indicated by the force vector 233. This vector may be resolved into its vertical component 235 and its horizontal component 23d. As the conveyor reverses its direction of travel at arrow 232 it exerts an upward acceleration force on the intermediate base. This force is counteracted by the equal and opposite force of the rotating weights as indicated by the force vector 236. This vertical force is in phase with the horizontal force 234 since both are being exerted by the same rotating unbalanced weights.

The amount of force to be exerted by the rotating unbalanced weights may be computed from the effective mass of the conveyor and the k or spring constant.

Since the conveyor rotates as it vibrates, the springs are subjected to torsion as well as simple bending which makes it di'icult to accurately compute their operational c or spring constant. To allow for small deviations between computed values and actual values, the ratio between the vertical and horizontal forces of the unbalanced weights is made adjustable. The amount or' vertical force in proportion to the horizontal force may be simply adjusted by adjusting the angle of the axis about which the unbalanced weight rotates.

This adjustment is made possible by making the position of the shafts 2tlg and 2l@ of the rotating weights adjustable with respect to the vertical axis of the conveyor and the mechanism employed for obtaining this adjustment is shown in detail in Fig. 7. The intermediate base i186 is shown with a projecting box 288 carrying a plate 2% for supporting the rotating cross shaft 216. The plate 29@ has holes 292 drilled at its corners for the receiving of bolts 294i. These bolts extend through arcuate slots 2% in a plate 29S which supports the gears for driving the shaft 2l@ on which are mounted the unbalanced weights. The plate 298 and shaft is rotationally adjustable with respect to the intermediate base by virtue of the arcuate slots 296 in the plate. The plate may be secured in any adjusted position by tightening the nuts (not shown) which are threaded to the bolts 29d. By the proper adjustment :of the angle of shafts 2% and 21@ the vertical component of force shown by 235 in Fig. l() may be adjusted to the proper magnitude to cancel out the vertical force of the conveyor as it reverses direction in the uppermost point in its travel. When the conveyor swings in the opposite direction and reaches the point indicated by the arrow 250, it reverses direction and exerts a downward force. This l@ downward thrust or acceleration or inertia force is' compensated for by the vertical component of force of the unbalanced weights which at this point is exerted in the upward direction.

Another feature to be noted, which is illustrated in Figs. 4, 6 and 8 is that a double spring may be used to support the intermediate base. A double spring makes it possible to use a shorter or lighter weight spring to obtain the same k factor. rihe use of a doutle spring allows use of smaller, less stiff springs decreasing stresses and thereby increasing the life of the spring. lt will also be noted in Figs. 4, 6 and 8 that the springs are preferably round in cross section. Because the springs must rotate or twist to accommodate the rotational movement of the conveyor while the intermediate base remains relatively stationary, a twist or torsional stress is exerted on the springs. Further since the end of the spring connected to the conveyor is at a fixed radius from the axis of the conveyor, this end moves inwardly and outwardly with respect to the end connected to the intermediate base or bends the spring in a radial direction. This may -be observed by projecting the ends of the springs connected to the conveyor on the horizontal plane of the spring ends connected to the intermediate base and it will be seen that the conveyor ends move radially with respect to lines tangential to the connecting points of the intermediate base ends. Thus the dat leaf Spring which is shown in Figs. l and 3 will be less resistant to the stress caused by the rotational vibration of the conveyor and will fail much more readily than the round spring. These springs may be solid or tubular.

Fig. 9 shows a detailed View of one means of attaching the springs to the members 19S which is the same fashion as the lower ends of springs attacher. to members 196. The ends of the beams 256 are flattened and half holes 25S are drilled in the edges of the ends so that when the edges of two beams are brought together a full size hole 26d is formed. The beam ends are secured against a flattened surface 264 of the tube S by bolts 262 which extend through a plate 2h55 placed over the beam ends. The bolts also extend through holes in the flattened surface 264 or" the tube and are secured by nuts threaded to the bolt ends.

The spring means, as shown in Figs. 6, S and 9, have an enlarged shoulder portion 2=38 at their ends at the point where the largest bending moment occurs and where failure or" the beam is most likely to take place. This greatly increases their life.

ln the conveyor of Fig. l1 another manner of applying a cyclical force to the intermediate base and of obtaining a canceling vertical force is shown. In this ernbodiment the conveyor is shown supported in a different manner, being supported by two pairs of first spring beams 274 and 276. Each pair is comprised of two identical springs such as is shown in Fig. 8. in this con-- struction, however, only two pairs are used being placed diametrically opposite from each other. These springs will of course have to have an individual spring constant or k factor higher than where three pairs are provided to obtain a proper torsional k for the system. To connect the springs to the conveyor Si?, a column 32@ extends from the top and is secured across tube 235 to which the first spring beams 274 and 226 connect. The connection between the springs and tube 2&6 is made by bolts 287 in the same manner as illustrated in Fig. 9. The springs are connected in the same manner at their upper ends to arms 282 and 28d which are welded to the intermediate base 272. Thus with this construction and the proper torsional k, only two sets of spring beams are necessary to support the conveyor.

The intermediate base 272 is supported from the floor by the second set of spring beams 2l, 283 and 235 which are vertical steel rods and are attached at their upper ends to the intermediate base. Their lower ends which are not shown rest on a base on the oor similar to the conveyors assale? conveyor, unbalanced weights 322 and 329 rotate on vertical shafts 326 and 323 respectively in the same manner as the weights in the embodiment shown in Figs. l

land 3. ,These vertical shafts carry pulleys Stili and 3d?.

at their lower ends to be driven by timing belts 3de and 396. The timing belts are driven by a double pulley 3,?3 carried on a shaft 310 drivenV by the motor Sii. The speed of the weights is adjusted so that they will rotate at the natural frequency of the system. The unbalanced weights, as Vwill be seen from the driving arrangement, rotate in the same direction and are arranged so that their radial forces cancel out and the forces tangential to the Vconveyor axis create a torsional force about the con-V veyor axis.

To cancel the vertical conveyor acceleration or inertia forces which occur both when the conveyor reachesthe extreme forward point of its travel and the extreme back point, a cyclical vertical force is Vapplied by unbalanced weights 313 and 314. These Weights are carried at the center of the intermediate baseon shafts 316 and 317. These shafts have weights on both ends although the weights at the rear of the shafts are hidden by the case l. The shafts driven through bevel gears within case 315 are driven by the shaft Siti which alsoJ drives the horizontal weights 322 and 32d. The phase of Weights 313 and al is so adjusted that it exerts a maximum ver- Y Vtical Vforce when the torque is exerted by the weights 322 and 321i.

When the conveyor has reached its maximum forward movement, moving in a clockwise direction looking upwardly in Fig. ll, the weights 322'and 321i exert a counterclockwise torque. The rotatingy weight 314 simultaneously exerts a vertical force in a downward direction to balance the upward force exerted by the deceleration of the conveyor as itrreverses direction.V When the conveyor reaches its bacl; position, the unbalanced weight 3314 exerts a force in the upward direction to compensate for the downward force caused by the conveyor in decelerating to reverse its direction.

The pairs of weights s and 314 rotate in opposite directions so that their horizontal forces cancel but their vertical forces add. VThey are balanced about thercenter of the intermediate base sothat no forces act through the axis of the conveyor and no unbalancing couples result.

will be seen in the embodiments shown in all the drawingsk that the conveyor as presented consists basically of the components including the conveyonrthe first and second spring beams, the intermediate oase and the cyclic force applying means. `While the dierent vembodiments shov-/nin the drawings include combinations of elements which vary in structure, it must be understood that the elements of the various Ycombinations shownL could be combined in different combinations. For. example, the unit shown in Fig. ll uses two sets of double springs. lt will be apparent from the principles taught by the present disclosure that the twoV sets of springs could be utilized in the embodiment of Fig. l instead of the iat spring beams therein used. Also elements of the embodiments shown in ligs. l, 4 or ll could be combined in various ways to utilize the advantages of a spiral conveyor' having two masses and two sets ,of supporting springs. y

As previously stated, the intermediate base in actual operation will have a small amountof motion due to frictional and damping losses of system. However, the amount'of motion will be relatively small and will be assimilated by the second set of spring beams supportingV the intermediate base andthe amount of force transmitted to 1g the. Suspertine member, i e, the floor 0rA ceiling. `will be practically Thus it ispossible to provide a vibratory conveyor without having a supporting structure which must sustain considerable reactance forces. It will be'further seen that in the embodiments of Figs. 4, 6 and ll that a means has been provided to cancel out thevertical acceleration forces of the conveyor. In helical conveyors heretofore used, these forcesphave not been successfully ,counteracted Y Thus it became necessary to provide a buildingV and a machine frame which was suiciently strong to assimilate these forces and in manycases the use of a vibratory conveyor was impractical. Thus by Vtheuse of a two-mass, two spring system, the forces transmitted to the support-V ing base have been reduced to an extremely small figure.

Thus we have made Vit possible for the lirst time to provide simple elective helical vibratory conveying action by the elimination of forces which normally are tran's mitted to the support. The vertical acceleration force components of the conveyor are counteracted at the intermediate base and are not transmitted to the ceiling` or Y oor support. With this system it is of course possible becauseof the elimination of these undesirable forces to Y yobtain a conveyor of a high degree of efliciency and one which can operate for a machine life that was previously unattainable. The `co-pending application, Vibratory Conveyors, George Long andiTaltuZo Tsuchiya, United States'Serial Number 329,556 illustrates a linear vibratory conveyor using a two-mass, two-spring system wherein undesirable forces have been counteracted in a horizontal vibratory conveyor.

VWe have,` in the drawings and specication, presented a detailed disclosure of the preferred embodiments of our invention. it isV to be understoodthat the inventionis susceptible of modifications, structural changes and various applications of use within the spirit and scope of the invention and We do not intend to limit the invention to the specific form disclosed but intend to cover all modications, changes and lalternative constructions and methods fallingwithin the scope of the principles taught by our invention.

We claim as our invention:

l. A vibratory conveyor comprising a conveying member having a spiral conveyor for conveying a solid material upwardly in a spiral path, an intermediate base member, a first set of spring beams inclined with respect tothe spiral path of feed up the conveying member and the opposite ends of said rst set of spring beams'being connected to said conveying member and base member respectively, atleast 'one end of each spring being rigidly connected, said first spring beams providing the soleload supporting connection for said conveying member andV permitting rotary oscillations of the conveying member Yabout its axis along an inclined path perpendicular tosaid Y beams, a second set of'beams extending vertically Vfrom said base member to support the weight of the conveying member andV associated apparatus, the end of said second set of beams yopposite said base member having means for attachment to a support, and means applying a cyclical torque solely to said basei member at a frequency relatively close to the natural frequency of the system consisting of the conveying member and first set of spring beams.

2.V A vibratory conveyorrcomprising a conveying member arranged in a spiral for conveying solid material, `an intermediate base member extending annularly around the spiral conveying member, a rst set of spring beams inclined with respect to the direction of feed along the conveying member and the opposite ends of said first set of spring beams being connected to said conveying member and base member respectively, at leastone end of each spring being rigidly connected, saidspring beams providing the sole load lsupporting connection for said conveying member and permitting oscillatory vibratory motion of the conveyor member about its central axis to convey the solids, a set of vertical support spring beams extending from said base member to a suitable support to support the intermediate base and its associated apparatus, said second set of beams being provided with means for attachment to said support, and means applying a cyclical force solely to said base member at a frequency relatively close to the natural frequency of the system consisting of the conveying member and said iirst spring beams.

3. A vibratory conveyor comprising a helical conveyor member for conveying solids upward along a helical path, an intermediate base arranged in the form of an annular frame encircling the conveyor, a Jrirst set of spring beams inclined with respect to the direction of feed of the solids 4on the conveyor and having their opposite ends connected to said conveying member and said base respectively to support the conveying member from said intermediate base, a second set of spring beams extending from said base member to support the base and its associated apparatus, and means applying a cyclical torque solely to said base at substantially the frequency of the natural frequency of the system consisting of the conveying member and first spring beams.

4. A vibratory conveyor comprising a conveying meniber conveying a solid material spirally upward, an intermediate base member, a first set of spring beams inclined with respect to the direction of feed of the material on the conveying member and having their opposite ends connected to said conveying member and base members respectively, said spring beams providing the sole load supporting connection for said conveying member and permitting oscillatory motion about a central axis to convey the material along the conveyor, a second set of spring beams connected to the intermediate base member and to a suitable stationary support to provide a sole support for the intermediate base member and associated mechanism, and means comprising at least one unbalanced rotating member dispaced from the central axis of the conveyor applying a cyclic torque about the central axis of the conveyor solely to said intermediate base member at a frequency relatively close to the natural frequency of the system.

5. A vibratory conveyor according to claim 4 wherein the axis of the unbalanced rotating member is at an angle to the vertical axis of the conveyor so that both a horizontal and a vertical component of force will be applied to the intermediate base by the rotating member.

6. A vibratory conveyor according to claim 4 wherein the axis of the unbalanced rotating member is at an angle to the vertical axis of the conveyor and the angle is of such a degree that the vertical components of force caused by the rotation of the unbalanced member will cancel the vertical acceleration forces of the vibrating conveyor.

7. A vibratory conveyor according to claim 5 `wherein the position of the axis of the unbalanced weight is adjustable to vary the ratio between the horizontal and vertical components of force created by the rotating unbalanced member for purposes of canceling varying vertical acceleration forces.

8. A vibratory conveyor according to claim 4 in which the means for applying a cyclic torque comprises rotating unbalanced weights, the axes of which re displaced from the axis of the conveyor and the angle of the axes is adjustable with respect to the conveyor axis to change the ratio between the horizontal and vertical force cornponents created by the unbalanced weights.

9. A vibratory conveyor according to claim 4 wherein a plurality of unbalanced weights is provided comprising a pair of rotating discs on each side of the conveyor being diametrically opposed and having unbalan-cing weights on the edge of the discs with the pairs of discs being driven from a common cross shaft and the axes of the discs being adjustable with respect to the axis of the conveyor by rotation about their centers.

l0. A vibratory conveyor comprising a spiral conveying member for carrying a solid material upwardly in a curvilinear path, an intermediate base member, a iirst set of spring beams inclined with respect to the direction of feed of material on the conveying member and having opposite ends connected to said base member and said conveying member respectively, said spring beams comprising the sole support for the conveying member,I a second set of spring beams substantially vertical and secured to the intermediate base providing the sole connection between said base member and a suitable stationary support, and a rotating unbalanced weight rotat-y ing about a vertical axis spaced from the conveyor axis, said weight applying a cyclical torque solely to said base member at a frequency relatively close to the natural frequency of the system consisting of the conveying member and first spring beams.

ll. A vibratory conveyor comprising a helical conveying member for conveying solid material up a spiral path, an intermediate base member, a first set of spring beams inclined with respect to the direction of feed on the conveying member and having their opposite ends connected to said conveying member and base member respectively and arranged about the axis of the conveying member, said springs being round in cross section to withstand the torsional stresses which occur as the conveyor rotates during vibration, a second set of spring beams secured to the base member and to a suitable supporting means to support the base member and associated mechanism, and means applying a cyclical torque solely to said base member at a frequency close to the natural frequency system consisting of the conveying member and first set of spring beams.

l2. A conveyor according to claim ll in which the ends of the round springs are larger than the centers to reduce the stress which normally occurs at the end of the spring to cause failure at that point.

13. A vibratory conveyor comprising a helical conveying member carrying a solid material from a lower to a higher level, an intermediate base member, a first set of spring beams inclined with respect to the path of material movement on the conveying member and having their opposite ends connected to said conveying member and base member respectively, said set of beams being arranged in pairs and the pairs being spaced around the axis of the conveying member, said iirst spring beams providing the sole load supporting connection for said conveying member and permitting oscillatory movement of the conveyor abo-ut said conveying member axis along an inclined path perpendicular to said beams, a second set of beams secured to said base member and extending to suitable support for carrying the conveying member and associated mechanism, and means applying a cyclical torque solely to said base member at a frequency relatively close to the natural frequency of the system consisting of the conveying member and first set of spring beams.

14. A vibratory conveyor according to claim 13 in which the pairs of spring beams are arranged by the members of each pair being positioned radially of each other with respect to the helical axis of the conveyor.

l5. A vibratory conveyor comprising a helical conveyor member conveying a solid material from a lower to a higher level, an intermediate base member, a first set of spring beams extending downwardly from the intermediate base member and arranged about the axis of the helical conveyor to support the conveyor, said beams being inclined to the path of feed of the solid material with at least one of the ends of the spring beams being rigidly connected, a second set of spring beams secured to the intermediate base and extending vertically to a suitable supporting member to support the base and its dependent mechanism, and means applying a cyclical torque to said intermediate base about the axis of the conveyor causing the conveyor to move in an oscillatory aszmsr 'i5 motion-in a path at right angles to the inclination `oflflrst said-spring-beams, the force being applied at a frequency relatively close to the natural frequency of the system including the conveyor and first spring beams.

16. A vibratoryV conveyor comprising a helical con-V veyor member carrying material fromta lower to a higher elevation, an intermediate base member, rst spring beams inclined with respect to the direction of feed of the material in its helical path and connected at opposite ends to the conveyor and to the intermediate base, a second set of spring beams extending vertically from the base and attached to a suitable supporting means above the intermediate base to furnish the sole support for the conveyor and associated mechanism, and means applying a cyclical force solely to the Vintermediatebase at a frequency relatively close to the natural frequency of the system consisting of the conveying member and first set of spring beams. Y i

17. A vibratory conveyor `comprising a helical conveying member conveying material from a lower to a higher elevation, an intermediate base member, a rst set of spring beams inclined with respect to direction of feed along a helical conveyor and attached at their opposite ends to the conveying member and base member respectively, said rst spring beams providing the sole load supporting connections for the conveying member and permittingL oscillatory motion of the conveyor `along, an inclined path perpendicular to said beams, the iirstspring beams comprising at least two beams arranged v'diametrically opposite each other with respect to the axis yof the helical conveyor, a second set of beams extending `substantially vertical fiom said intermediate base to a suitable supporting member and'comprisingtthe sole support for the intermediate base, and means applying a cyclical torque about the Vaxis of the helical conveyor at a frequency relatively close to the natural frequency of the system consisting of the conveying member and rst set of spring beams.

18. A vibratory conveyor comprisingV a helical conveying member conveying material from a lower to a higher level, an intermediate baselmembe'r, a first set of spring beams extending between the base member and conveyor to comprise the sole support for the conveyor with the opposite ends connected to the base member and lconveyor respectively, saidhrst spring Vbeams inclined with respect to the path of feed ofthe conveyed material, a second set of spring beams extending vertically from 'the intermediate base member to a suitablesupport and comprising the support for the intermediate base and associated mechanism, means applying a cyclical torque to said base member about the axis of the conveying member and applying said force at a frequency relatively close to the natural frequency of the system consisting of the conveying member andrirst set of spring beams,'said force applying means oscillating the helical conveyor about its helical axis in a path perpendicular to said first set of spring beams, and a second cyclical force applying means applying a force in a plane parallel to the helical axis and at a frequency equal to the frequency of said first cyclical force to counterbalance the vertical acceleration forces of the vibrating conveying member. Y

19. A vibratory conveyor comprising a helicalV conveying unit conveying material from a lower to a higher levelfan intermediate base member, a rst setcf spring beams inclined with respect to the direction of feed of the material on the helical conveying unit` and having their opposite ends connected to the conveying unit and base member, a second set of spring beams extending vertically from the intermediaterbase to a suitable support, and means mounted on the intermediate base and applying a cyclical torsional force about the axis of the helical conveyor at a frequency7 relatively close to the natural frequency of the system consisting of the conveying member and first set of spring beamsthe force applying means comprising a pair of unbalanced weights rotating aboutl a'vel'tcal axis at .the same frequency andcqually and di-Y ametrically spaced from theY axis of theuhelical conveyor and rotating in the same direction but l" out of phase so aswto cancel forces radial to the conveyor axisvand addl forces tangential to the conveyor toccreate atorque about' the conveyor axis. y g Y 20A vibratory conveyor comprising a helical conveying unit conveying material from'a lower to a higher level, an intermediate basevmember, a first set of spring beams inclined with'respect to the direction of feed of the material on the helical conveying unit Vand having their opposite ends respectively connected to the convey-V ing unit and intermediate base, said springcbeams comprising the sole support for the conveying unit, a resilient Y support for said intermediate base and its associated mechanism and beinguconnected between the resilient base andV a suitable supportingunit, the resilient support ab-l sorbing small movements of the intermediateb'a'se cushioning the forces transmitted to said supporting unit, and means for applying a cyclicaltorque about the axis of the helical conveyor at a frequency relatively close to the natural frequency of the system consisting` ofthe conveying member and a first set of spring beams, and means for applying a second cyclical force at the same'frequency as said cyclical torque which is the frequency of vibration of the conveyor, saidY second force-applying means acting in a vertical directionY to counteract kthe vertical acceleration forces created bythe conveyor as it reverses direction during vibration. Y

2l. A vibratory conveyor comprising a helical conveying member elevating a solid material, an intermediate base member, a set of spring. beams inclined with respect to the direction of feed of the material on the conveying member and having the individual beam ends connected to the conveying unit and intermediate base member to provide the sole support for the conveying member, a support for the intermediate base extending'vbetween the base and a suitable carrying means, said support being resilient about a vertical axis coicident Vwith theraxis of the conveyor toV permittorsional movement of the intermediate base, and means applying a torque about the axis of the conveyorV to the intermediate base at a frequency relatively closed to the natural frequency of the system consistingv of the conveying member and spring beams. c i Y 22. A vibratory conveyorl comprising a helicalV conveying member conveying material from a lower'to a higher level, an intermediatebase member, aset of spring beams inclined with respect to the Vdirection, offeed of the material on the helical conveyor and arranged about the conveyor with their ends connected to the conveyor and intermediate base to comprise the sole support for the conveyor, aV resilient supportv for the intermediate base to form the sole means of support between the base and a suitable carrying element permitting resilient movement of the oase as the conveyor operates, and means mounted on the intermediate base and applying a cyclical torque about the conveyor axis at a frequency relatively close to the natural frequency of the system including the conveying member and the first set'of spring beams, and rotatingV unbalanced weights rotating in opposite directions and having their combined center of gravity substantially at the axis of the conveyor and rotating at the Y frequency of the cyclical torque-applying means to apply a vertical force to cancel out the vertical forces of the conveyor as it vibrates.

23` A vibratory conveyor comprising arhelical conveying unit elevating a solid material, an intermediate base member, a rst set of spring beams Ainclined with respect to the direction of feed of the material on the conveying member and extending upwardlyfrom the inter- Y mediate base to be secured to the'conveyor and comprising thek sole support for the conveyor, a second set of spring beams rkextending from Vthe intermediatejbase to a suitable support and comprising'the sole support for `said base and associated mechanism, and means supported on the intermediate base and applying a cyclical torque thereto operating at substantially the natural frequency of the system consisting of the conveying member and iirst set of spring beams.

24. A vibratory conveyor comprising a helical conveying member for elevating material, an intermediate base member, a tirst set of spring beams positioned at an angle less than perpendicular to the direction of feed of the material and having their ends secured to the conveyor and the intermediate base, a second set of spring beams extending substantially vertically from the intermediate base to a suitable support, and means mounted on the intermediate base and applying a cyclical torque to the intermediate base about the axis of the conveying member, and a vertical force-applying means mounted on the intermediate base comprising at least two rotating weights rotating on horizontal axes and positioned equidistant from the center of the conveyor, means to rotate the Weights in an opposite direction so that they will exert cyclic forces at the frequency of vibration of the conveyor and in a direction to exert vertical forces to cancel the vertical acceleration forces of the conveyor.

References Cited in the ile of this patent UNITED STATES PATENTS 2,658,286 Spurlin Nov. 10, 1953 

